DE102020113128A1 - Bearing arrangement - Google Patents

Abstract

The invention relates to a bearing arrangement formed from a shaft and a roller bearing, in particular with the connection of roller bearing and shaft. For this purpose, a bearing arrangement is specified which comprises a roller bearing 1, which consists of an inner bearing ring 2 completely traversed by an axial bore 9, an outer bearing ring 3 and between the two bearing rings 2, 3 on raceways 5 rolling elements provided by the bearing rings 2, 3 4 comprises, wherein at least the inner bearing ring 2 comprises at least two segments 13 which are radially divisible, and wherein a shaft 10, which penetrates the axial bore 9 of the inner bearing ring 2 and forms a non-rotatable connection with the inner bearing ring 2 when the inner Bearing ring 2 is connected to the shaft 10. In order to improve the connection between the shaft 10 and the inner bearing ring 2, the shaft 10 has a uniformly large diameter D1 in an axial region 11, which is intended to accommodate the roller bearing, and the axial bore 9 has a diameter D1 at its axial ends 8.3, 8.4 Diameter D2, which is greater than the diameter D3 of the axial bore 9 centrally between its axial ends 8.3, 8.4. Alternatively, the axial bore 9 can have a uniformly large diameter D1 'and the axial area 11 of the shaft 10, which is intended for receiving the roller bearing 1, has a diameter D2' at its axial ends 8.85, 8.6 which is smaller than the diameter D3 'between these axial ends 8.5, 8.6.

Description

Technical area

The invention relates to a bearing arrangement formed from a shaft and a roller bearing, in particular with the connection of roller bearing and shaft.

If a shaft is to be rotatably arranged in the shaft of a connecting structure that surrounds it, it is usual to provide a bearing between the shaft and the connecting structure. This bearing can be a plain bearing or a roller bearing. Rolling bearings to which this application relates generally have an inner bearing ring, an outer bearing ring surrounding the inner bearing ring with a radial spacing, and rolling elements which roll on raceways provided by the bearing rings. The inner bearing ring is traversed between its axial ends by a bore which is penetrated by the shaft when the bearing arrangement is mounted.

As a rule, the outer bearing ring is held in a rotationally fixed manner by a recess in the connecting structure that is adapted to the shape of the outer bearing ring. In order to connect the inner bearing ring to the shaft in a rotationally fixed manner, the inner bearing ring can be fixed between a shaft shoulder and a shaft nut. It is also known to shrink the inner bearing ring onto a shaft by heating the inner bearing ring and positioning it on the shaft in this state so that an interference fit is established between the shaft and the inner bearing ring after the inner bearing ring has cooled down.

These types of connection between the inner bearing ring and shaft are usually used when the respective bearing ring has a closed ring shape and there is no need to fear that the rolling bearing will have to be replaced, for example due to wear.

However, there are many systems with a service life of 20 or more years, so that a wear-related replacement of rolling bearings during the planned service life is unavoidable. If the systems and rolling bearings are very large, it is often very time-consuming to replace the rolling bearings. So it cannot be ruled out that large and heavy add-on and conversion parts have to be removed beforehand to replace bearings and / or the supported shaft has to be lifted a little. Such a bearing exchange turns out to be particularly complex if the systems are offshore systems, for example in the form of wind turbines, because then floating cranes are usually required to lift the shaft.

Therefore, one has gone over to design the bearing rings in a modular manner.

Such an arrangement is in DE102016213861 A1 shown. In this arrangement, the inner and the outer bearing ring are each formed by two half-shell-shaped segments. In order to produce a non-rotatable connection of the two half-shell-shaped segments forming the inner bearing ring with the shaft, half-shell-shaped tensioning straps are also placed around the inner bearing ring. If screws are tightened that are passed through the tensioning straps, the diameter of the two tensioning straps loosely placed around the two segments of the inner bearing ring is reduced. This leads to the segments forming the inner bearing ring being pressed against the shaft and thus the segments or the inner bearing ring formed from them being fixed on the shaft in a rotationally fixed manner.

If the inner bearing rings formed from the half-shell-shaped segments have a large axial length or if these bearing rings belong to rows of widths 240, 241 or 249, undesired rotation of the inner bearing rings around the shaft cannot be completely ruled out if the roller bearing is loaded during operation will.

The invention is therefore based on the object of preventing inner bearing rings formed from segments from rotating on the shaft under operating conditions.

Presentation of the invention

This object is achieved with the features specified in claim 1. Advantageous designs and developments of the invention can be found in claims 2 to 5.

If the shaft has a uniformly large diameter D1 in an axial area intended for receiving the roller bearing, and the diameter D2 at the axial ends of the axial bore is greater than the diameter D3 of the axial bore centrally between its axial ends, or has the axial bore in the inner bearing ring has a uniform large diameter D1 'and the axial area of the shaft, which is intended to receive the roller bearing, has a diameter D2' at its axial ends, which is smaller than the diameter D3 'between these axial ends is at Connecting the shaft and the inner bearing ring at the axial ends of the bore creates a radial distance A. This distance A can be used to even out the pressing forces that the inner bearing ring formed from segments exerts on the shaft over the axial length of the inner bearing ring when forces are exerted by the Differences in diameter D1 to D2 or D1 'to D2' have an effect on the resulting distance A and eliminate this distance A.

It is advantageous if a contour line, which extends between the axial ends of the axial bore or the axial ends of the axial region of the shaft, has an arcuate course, because such a contour line appears in a rolling movement after the action of forces on the distance A creates the other partner.

Impairments to the raceways on the inner bearing ring are excluded if the roller bearing is a double row tapered or spherical roller bearing and the largest diameters D3, D3 'of the axial bore or the axial area between the two rows of tapered or spherical roller bearings lie. If the axial extent of the inner bearing ring is greater than the axial extent of the outer bearing ring, these axial protrusions of the inner bearing ring compared to the outer bearing ring provide sufficiently large leverage ratios to allow force-related contact between the respective partners, even with massive inner bearing rings, eliminating the distance A to manufacture.

It is advantageous if clamping bands are placed around the axial protrusions between the inner bearing ring and the outer bearing ring, which, when the respective roller bearing is connected to the shaft, exert a pressing force on the protrusions and thus connect the axial ends of the bore or the axial area of the shaft to the bring each other partner in contact.

Figure list

• 1 eine Lageranordnung im Seitenschnitt,
• 2 eine weitere Darstellung gemäß 1, und
• 3 eine weitere Ausführungsform einer Lageranordnung

Show it:

• 1 a bearing arrangement in side section,
• 2 a further representation according to 1 , and
• 3 another embodiment of a bearing arrangement

Ways of Carrying Out the Invention

In 1 is a rolling bearing 1 shown in the form of a double row spherical roller bearing. These spherical rollers are supported by an inner bearing ring 2 and an outer bearing ring 3 formed, the outer bearing ring 3 the inner bearing ring 2 surrounds coaxially. Between the two bearing rings 2 , 3 roll rolling elements 4th up from the bearing rings 2 , 3 provided careers 5. Due to the fact that the in 1 rolling bearings shown 1 is a double row spherical roller bearing, the outer bearing ring 3 a unified career 5.1 on while the inner bearing ring 2 for each of the two rows of rolling elements 6.1 , 6.2 a separate career 5.2 , 5.3 having. As shown in the illustration 1 is easily removed, the two raceways are in this embodiment 5.2 , 5.3 on the inner bearing ring 2 from a central shelf 7th separated from each other, the one between the two rows of rolling elements 6.1 , 6.2 engages and with the inner bearing ring 2 forms an integral unit.

The inner bearing ring 2 is between its two axial ends 8.1 , 8.2 from a hole 9 completely traversed. To form a bearing assembly, the bore 9 from a cylindrical shaft 10 penetrated, at least in the axial area 11th the wave 10 , which in the assembled state of the shaft 10 and rolling bearings 1 from the inner bearing ring 2 is covered, has a uniformly large diameter D1. In contrast, is the diameter of the axial bore 9 in the direction of their axial extent is not uniformly large, but has near their axial ends 8.3 , 8.4 a diameter D2, which is slightly larger than the diameter D3 of the axial bore 9 between their two axial ends 8.3 , 8.4 is. Like the representation according to 1 clearly shows, has the contour line corresponding to these diameter specifications in this exemplary embodiment 12th the axial bore 9 a slightly arched course. Since i.ü. the diameter D1 of the shaft 10 the diameter D3 of the axial bore 9 corresponds, this has the consequence that only the axial ends 8.3 , 8.4 the axial bore 9 each a small radial distance A to the shaft 10 adhere to when the wave 10 from the axial bore 9 is recorded.

Since it is decisive on the small radial distance A between shaft 10 and axial bore 9 near the axial ends 8.3 , 8.4 arrives, the curved course of the contour line 12th also the inner contour of the axial bore 9 In another, not shown embodiment of two cones, the respective small diameter sides in the middle of the axial bore 9 merge.

Even if in connection with this registration of bearing rings 2 , 3 is talked about, are the bearing rings 2 , 3 no one-piece components. Rather, it is the bearing rings 2 , 3 For the purposes of this application, it is modular, made up of segments 13.1 , 13.2 formed bearing rings 2 , 3 . According to the illustration according to 1 becomes each of the two bearing rings 2 , 3 of two half-shell-shaped segments 13.1 , 13.2 educated. This half-shell-shaped formation of the segments 13.1 , 13.2 allow easy replacement of the bearing rings 2 , 3 because the segments 13.1 , 13.2 radial from the shaft 10 can be removed and connected to it without the shaft 10 needs to be expanded. the end for this reason one also speaks of radially split bearing rings 2 , 3 .

Furthermore, according to the illustration 1 it can be seen that the axial extent E1 of the outer bearing ring 3 compared to the axial extent E2 of the inner bearing ring 2 is less. This is opposite to the outer bearing ring 3 on each side of the inner bearing ring 2 an axial protrusion 14th a. To these overhangs 14th around it are two half-shell-shaped tightening straps 15th arranged. Is done by tightening the screws 16 the respective diameter D4 of the tightening straps 15th is decreased, the radial distance A between the axial ends is reduced 8.3 . 8.4 the axial bore 9 and the wave 10 eliminated so that the diameter D2 corresponds to the diameter D1 and extends over the entire axial length of the axial bore 9 with which this on the shaft 10 is applied, a press connection is set. Such relationships are 2 shown.

That in 3 execution game shown differs from the embodiment according to 1 in that the axial bore 9 in the inner bearing ring 2 between their axial ends 8.3 , 8.4 has a uniformly large diameter D1 'and that the axial region 11' of the shaft 10 which in the connected state of shaft 10 and inner bearing ring 2 from the inner bearing ring 2 is covered at its axial ends 8.5 , 8.6 a diameter D2 'which is smaller than the diameter D3' between these axial ends 8.5 , 8.6 is. Consequently, in this exemplary embodiment, the radial distance A is not reduced by reducing the diameter D2 at the bore 9 compared to the diameter D1 of the shaft 10 but vice versa by reducing the diameter D2 'of the shaft 10 compared to the diameter D1 'of the bore 9 educated. Because of the reversal of the ratios, the situation in this exemplary embodiment is not as in FIG 1 the diameter D3 of the hole 9 but the diameter D3 'of the shaft 10 radially opposite the central rim 7th when the tightening straps 15th not through the screws yet 16 are attracted.

List of reference symbols

1

roller bearing

2

inner bearing ring

3

outer bearing ring

4th

Rolling elements

5.1 ... 5.n

career

6.1, 6.2

Rolling element series

7th

Center board

8.1 ... 8.n

axial end

9

drilling

10

wave

11th

axial area

12th

Contour line

13.1, 13.2

segment

14th

Got over

15th

Tension band

16

screw

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• DE 102016213861 A1 [0007]

Claims (5)

Bearing arrangement with a roller bearing 1, which is formed from an inner bearing ring 2 completely traversed by an axial bore 9, an outer bearing ring 3 and between the two bearing rings 2, 3 on raceways 5.1, 5.2, 5.3 rolling elements 4 that roll off the bearing rings, wherein at least the inner bearing ring 2 has at least two segments 13.1. 13.2, which are radially divisible, and with a shaft 10 which penetrates the axial bore 9 of the inner bearing ring 2 and forms a rotationally fixed connection with the inner bearing ring 2 when the inner bearing ring 2 is connected to the shaft 10, characterized in that, that the shaft 10 has a uniformly large diameter D1 in an axial region 11, which is intended to accommodate the roller bearing 1, and the diameter D2 at the axial ends 8.3, 8.4 of the axial bore 9 is greater than the diameter D3 of the axial bore 9 in the middle between the axial ends 8.3, 8.4, or that the axial bore 9 has a uniformly large diameter D1 'and the axial region 11 of the shaft 10, which is intended to accommodate the roller bearing 1, has a diameter D2 at its axial ends 8.5, 8.6 'which is smaller than the diameter D3' between these axial ends 8.5, 8.6. Bearing arrangement according to Claim 1 characterized in that a contour line 12, which extends between the axial ends 8.3, 8.4 of the axial bore 9 or the axial ends 8.5, 8.6 of the axial region 11 of the shaft 10, has an arcuate course. Bearing arrangement according to Claim 1 or 2 characterized in that roller bearing 1 is a double row tapered or spherical roller bearing and that the largest diameters D3, D3 'of the axial bore 9 or the axial area 11 are between the two rows of rollers 6.1, 6.2 of tapered or spherical roller bearings. Bearing arrangement according to one of the Claims 1 until 3 characterized in that the axial extent E1 of the inner bearing ring 2 is greater than the axial extent E2 of the outer bearing ring 3 and, as a result, the inner bearing ring 2 provides axial protrusions 14 relative to the outer bearing ring 3. Bearing arrangement according to Claim 4 characterized in that around the axial protrusions 14 between the inner bearing ring 2 and the outer bearing ring 3 clamping bands 15 are placed, which in the connected state of the respective roller bearing 1 with the shaft 10 exert a pressing force on the protrusions 14 and thus the axial ends 8.3, 8.4; 8.5, 8.6 of the bore 9 or the axial area 11 of the shaft 10 with the other partner 9; 10 bring in contact.

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